Pellet transfer apparatus and method

ABSTRACT

An apparatus for transferring a mold charge pellet to a molding machine having a mold with a mold cavity includes a hub rotated about an axis, at least one arm extending generally radially from the hub to rotate with the hub around the axis, and a cam system extending at least partially around the axis and operably coupled to the arm for moving the arm along a predetermined path with respect to the axis as the hub and the arm rotate around the axis. In one presently preferred embodiment, at least a portion of the arm traveling along a plane that is parallel to the axis during a portion of said path.

FIELD OF THE INVENTION

This invention relates generally to molding plastic articles and moreparticularly to an apparatus for providing charges of plastic to amolding machine.

BACKGROUND OF THE INVENTION

Various plastic articles, such as plastic closure for containers, havebeen formed by a compression molding process. Some compression moldingmachines have a plurality of tools mounted in a circumferential array ona rotatable turret in a plurality of opposed coacting pairs. The toolsof each pair carry opposed male and female mold sections that whenclosed together form a cavity in which plastic articles may becompression molded. During a portion of the rotation of the turret, themold tooling pairs are moved toward each other for compression moldingarticles between the tooling pairs and away from each other forreleasing articles molded between the tooling pairs and to receive freshcharges of plastic into the mold cavities. The charges of plastic may betaken and delivered from a stream extricate from an extruder providing arelatively rapidly available supply of plastic material for the moldingmachine.

SUMMARY OF THE INVENTION

An apparatus for transferring a mold charge pellet to a molding machinehaving a mold with a mold cavity includes a hub rotated about an axis,at least one arm extending generally radially from the hub to rotatewith the hub around the axis, and a cam system extending at leastpartially around the axis and operably coupled to the arm for moving thearm along a predetermined path with respect to the axis as the hub andthe arm rotate around the axis. In one presently preferred embodiment,at least a portion of the arm travels along a plane that is parallel tothe axis during a portion of said path.

In one implementation, the molding machine includes a turret rotatedabout an axis that is parallel to the axis about which the hub rotates.A plurality of molds are carried by the turret for movement in anendless path with each mold preferably including at least one radiallyaligned pair of mold cavities. Correspondingly, each arm of theapparatus preferably includes two sets of tooling with each set adaptedto deliver a separate mold charge pellet into a separate one of the moldcavities. To facilitate aligning the tooling sets with the moldcavities, the arm is preferably angularly, radially and axially pivotedrelative to the hub. According to one presently preferred aspect, apoint midway between the tooling sets on each arm is moved along a planeduring a portion of the movement of the arm wherein the mold chargepellets are transferred to the mold cavities. The planar motionpreferably includes an axially component wherein the arm is movedaxially toward the mold cavities to facilitate releasing the mold chargepellets from the tooling.

BRIEF DESCRIPTION OF THE DRAWINGS

These and other objects, features and advantages of the presentinvention will be apparent from the following detailed description ofthe preferred embodiments and best mode, appended claims andaccompanying drawings in which:

FIG. 1 is a perspective view of one presently preferred embodiment of anapparatus for compression molding plastic articles including onepresently preferred embodiment of a pellet cutter and transferapparatus;

FIG. 2 is a perspective view of the pellet cutter and transfer apparatusof FIG. 1;

FIG. 3 is a plan view illustrating an extruder and the pellet cutter andtransfer apparatus;

FIG. 4 is a plan view of the pellet cutter and transfer apparatus with aportion of a frame of the apparatus removed;

FIG. 5 is a perspective view of one arm and associated tooling of thepellet cutter and transfer apparatus;

FIG. 6 is a rear perspective view of the arm shown in FIG. 5;

FIG. 7 is a side view of the arm;

FIG. 8 is a plan view of the arm;

FIG. 9 is a side view of a base plate of the arm;

FIG. 10 is a perspective view of a second plate of the arm;

FIG. 11 is a side view of the second plate;

FIG. 12 is a plan view of the second plate;

FIG. 13 is a perspective view of a third plate of the arm;

FIG. 14 is a side view of a third plate;

FIG. 15 is a plan view of the third plate;

FIG. 16 is an end view of the third plate;

FIG. 17 is a perspective view of a gripper latch of the arm;

FIG. 18 is a side view of the gripper latch;

FIG. 19 is a bottom view of the gripper latch;

FIG. 20 is a perspective view of one embodiment of a lift latch;

FIG. 21 is a side view of the lift latch;

FIG. 22 is a plan view of the lift latch;

FIG. 23 is a view of the lift latch taken in the direction of the arrows23-23 in FIG. 22;

FIG. 24 is a bottom view of a cam plate assembly of the pellet cutterand transfer apparatus;

FIG. 25 is a side view of the cam plate assembly;

FIG. 26 is another side view illustrating a different portion of the camplate assembly;

FIG. 27 is a side view illustrating yet another portion of the cam plateassembly;

FIG. 28 is a perspective view of the tooling on an arm of the pelletcutter and transfer apparatus;

FIG. 29 is a side view of a two sets of tooling carried by the arm ofthe pellet cutter and transfer apparatus;

FIG. 30 is a plan view of the tooling;

FIG. 31 is a perspective view of an alternate embodiment of a liftlatch;

FIG. 32 is a side view of the lift latch of FIG. 31;

FIG. 33 is an end view of the lift latch;

FIG. 34 is a diagrammatic view illustrating the movement of an arm ofthe pellet cutter and transfer apparatus relative to an axis about whichthe arm is driven;

FIG. 35 is a diagrammatic view illustrating the movement of an arm ofthe pellet cutter and transfer apparatus relative to the axis aboutwhich the arm is driven and relative to the path of travel of moldcavities of a molding machine; and

FIG. 36 is a fragmentary side elevational view of illustrating a portionof an arm of the pellet cutter and transfer apparatus according to analternate embodiment of the invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring in more detail to the drawings, FIG. 1 illustrates a system 10for compression molding plastic articles such as preforms that aresubsequently molded into plastic containers. The system 10 includes acompression molding machine 14 that preferably includes a rotary turret16 with a plurality of pairs of mold tooling 18 disposed about theperiphery of the turret 16 in an endless path (in FIG. 1, some moldtooling pairs have been removed to show the turret 16). An extruder 20provides molten plastic material that is delivered to the mold toolingpairs 18 to form the plastic articles. The extruded material isdelivered to the mold cavities 24 by a pellet cutter and transferapparatus 26 that preferably accurately cuts the extruded material 20into desired sized mold charge pellets 28 (FIG. 35) and delivers thepellets 28 or plastic charges into cavities 24 of the mold tooling pairs18. The mold tooling pairs 18 may be constructed and arrangedsubstantially as shown and described in U.S. patent application Ser. No.______ and the rotary turret 16 and associated components can beconstructed and arranged as shown and described in U.S. patentapplication Ser. No. ______. A take-out mechanism 30 is preferablyprovided to remove formed plastic articles from mold cavities 24 and totransfer them away from the compression molding apparatus 14 for furtherprocessing, such as either cooling or subsequent blow molding. A takeoutand cooling apparatus as shown and described in U.S. patent applicationSer. No. ______ may be provided.

Desirably, the mold tooling pairs 18 are open during a portion of therotary movement of the turret 16 to permit the formed plastic articlesto be removed from and fresh mold pellet charges 28 to be delivered intothe mold cavities 24. To increase the productivity and efficiency of thesystem 10, the mold tooling pairs 18 are preferably separated for alimited duration of the molding cycle. This increases the time duringthe cycle for compression molding and permits an increased rotary speedof the compression molding apparatus 14. Accordingly, in one presentlypreferred embodiment, the pellet cutter 26 is constructed and arrangedto be disposed generally beneath at least a portion of the take-outapparatus 30 so that as the take-out apparatus 30 is removing plasticarticles from the tooling pairs 18, the pellet cutter and transferapparatus 26 is delivering fresh plastic charges 28 into the moldcavities 24.

As best shown in FIGS. 2-4, the pellet cutter and transfer apparatus 26preferably includes a main frame 36 having a base 38, a plurality ofposts 40 extending from the base 38 and interconnected by appropriatebeams 42 and cross supports 44 providing a ridged structure. Desirably,an end 48 of the extruder 20 including a pair of outlets 50 of theextruder 20 is carried on a sub frame 52 mounted on the base 38 forcommunication with the pellet cutter and transfer apparatus 26.Desirably, the mold tooling 18 of the compression molding apparatus 14includes mold cavities 24 in radially aligned pairs, and the extruderoutlets 50 provide two streams of extruded material 20 that are meteredand delivered by the pellet cutter and transfer apparatus 26.

The pellet cutter and transfer apparatus 26 includes a main shaft 54driven for rotation about its longitudinal axis 56 by a motor 58 throughan appropriate gear box 60 mounted on the base 38. The shaft 54 ispreferably journalled for rotation by bearings 62 disposed in a collar64 that may be fixed to the frame 36. A hub 66 is operably connected tothe shaft 54 for co-rotation with the shaft 54 relative to the frame 36and the extruder outlets 50. The hub 66 preferably includes a pair ofaxially spaced plates 68. At least one and preferably a plurality ofarms 70 extend generally radially outwardly from the hub 66, areconnected at one end 146 to the hub 66 for rotation with the hub 66, andare generally free at their other end 144. The arms 70 preferablyinclude two sets of tooling 72 with each set of tooling 72 being alignedwith one of the outlets 50 of the extruder 20 to cut pellets 28 from theassociated stream of extruded material 20 and carry and deliver thepellets 28 to the compression molding machine 14.

A cam system 74 (FIGS. 24-27) is carried by the frame 36 and operablyassociated with the arms 70 such that the arms 70 are displaced relativeto the hub 66 as the hub 66 and the arms 70 are rotated relative to thecam system 74. Desirably, each arm 70 includes at least one andpreferably a plurality of followers that are responsive to the contourof one or more cam surfaces on the cam system 74 to provide a desiredradial, axial and angular motion of each arm 70 relative to the extruderoutlets 50, as well as to the mold cavities 24 of the compressionmolding machine 14. Preferably, during at least a portion of therotation of the hub 66, each set of tooling 72 on an arm 70 is axiallyaligned with a cavity 24 of a mold tooling pair 18. Preferably, as willbe set forth in more detail below, the arms 70 are driven so that thepath of travel of the sets of tooling 72 matches or is closely alignedwith the path of travel of the mold cavities 24 along a desired angularextent of the rotation of the compression molding turret to facilitatedelivery of the plastic charges into the mold cavities 24.

As best shown in FIGS. 6-9, each pellet cutter arm 70 includes a baseplate 78 extending laterally with an angled or generally transversesupport 80 terminating in a cylindrical and tubular wall 82. A pivotshaft 84 is journalled for rotation in the cylindrical wall 82, such asby needle bearings 76, preferably with opposed ends of the shaft 84extending axially from the cylindrical wall 82. In this manner, thepivot shaft 84 can be coupled to or carried by the upper and lowerplates 68 of the hub 66 to define a pivot axis 86 about which the arm 70pivots. The pivot axis 86 is preferably parallel to the rotational axis56 of the main shaft 54, which is likewise parallel to the rotationalaxis 88 (FIGS. 1 and 35) of the turret 16 of the compression moldingmachine 14. In this manner, the arm 70 is mounted to the hub 66 by atrunnion-like arrangement permitting relatively free pivotal or angularmovement of the arm 70 relative to the hub 66. As best shown in FIG. 9,the base plate 78 preferably includes a pair of laterally extending andparallel rails 92 on which are mounted suitable slide blocks 94providing linear bearings carried by the base plate 78. The linearbearings are preferably arranged generally perpendicular to the pivotaxis 86 of the base plate 78. A laterally extending flange 96 preferablyincludes a first cam follower 98 rotatably carried on a shaft 99 fixedto the flange 96. The first cam follower 98 is responsive to the contourof a corresponding cam surface or cam track of the cam system 74 topivot the base plate 78 about the pivot axis 86 as desired.

As best shown in FIGS. 5-8 and 10-12, an intermediate plate 100 ispreferably mounted to the base plate 78 by the blocks 94 such that theintermediate plate 100 is slidably carried by the base plate 78. Aplurality of fasteners may be disposed through a plurality of bores 106in the intermediate plate 100 to connect the intermediate plate 100 tothe blocks 94 of the base plate 78. Desirably, the intermediate plate100 slides laterally relative to the base plate 78 in a direction thatis generally perpendicular to the pivot axis 86. The intermediate plate100 includes an outwardly extending bracket 108 with a second camfollower 110 rotatably mounted on a shaft 109 carried by the bracket108. The second cam follower 110 is responsive to the contour of acorresponding cam surface of the cam system 74 to slidably move theintermediate plate 100 relative to the base plate 78 as desired. Theintermediate plate 100 also includes at least one and preferably a pairof rails 111 with each rail 111 including at least one block 112slidably mounted on the rail 111 defining a linear bearing. Preferably,each rail 111 extends parallel to the pivot axis 86 and generallyperpendicular to the rails 92 on the base plate 78. The intermediateplate 100 may include outwardly extending flanges 113 with through holes114 adapted to receive support shafts 115 about which springs 116 may bemounted.

A generally U-shaped cam plate 118 having a contoured cam surface 119 ispreferably carried by the intermediate plate 100. The cam plate 118 ispreferably adjustably carried by the intermediate plate 100 by retainingblocks 120 fixed to the intermediate plate 100 and including opposedinwardly facing flanges 121 that overly adjacent portions of the camplate 118 to retain the cam plate 118. An adjustable mounting block 102,such as a jack block 122, is preferably carried in a slot 123 of theintermediate plate 100 to permit lateral adjustment of the cam plate 118relative to the intermediate plate 100 via a jack screw 124.

As best shown in FIGS. 5-8 and 13-16, each arm 70 preferably includes athird plate 125 that is carried by the intermediate plate 100. The thirdplate 125 is preferably fixed to the blocks 112 of the linear bearingson the intermediate plate 100 so that the third plate 125 can beslidably displaced relative to the intermediate plate 100 along therails 111. Accordingly, the intermediate plate 100 is slidably moveablein a direction parallel to the pivot axis 86. The third plate 125includes an upstanding bracket 126 on which a third cam follower 127 isrotatably mounted by a shaft 128 carried by the bracket 126. The thirdcam follower 127 is responsive to the contour of a corresponding camsurface or cam track of the cam system 74 to slidably displace the thirdplate 125 relative to the intermediate plate 100 and base plate 78, asdesired.

A lateral slide 129 is preferably slidably carried by the third plate125 through appropriate bearings or blocks 130 (FIG. 13) carried by thethird plate 125. The slide 129 preferably extends generallyperpendicular to the pivot axis 86 and hence perpendicular to themovement of the third plate 125 relative to the intermediate plate 100.The slide 129 preferably includes a fourth cam follower 131 rotatablycarried by a shaft fixed to a flange 132 of the slide 129. The fourthcam follower 131 is responsive to the contour of a corresponding camsurface or cam track of the cam system 74 to drive the slide 129relative to the third plate 125 in a direction generally perpendicularto the pivot axis 86. A block 133 carried by the slide 129 may bereceived in a slot 134 formed in the third plate 125 and engageable withthe end of the slot 134 to limit the movement of the slide 129 relativeto the third plate 125. As will be discussed in more detail hereafter,one section of each set of tooling 72 is preferably fixed to the thirdplate 125 and another section of each set of tooling 72 is preferablycarried by the slide 129 for movement with the slide 129 relative to theother section to open and close the sets of tooling 72.

As best shown in FIGS. 15 and 16, a fifth cam follower 135 is preferablyrotatably carried by a shaft fixed to the third plate 125 for rotationabout an axis 136 generally perpendicular to the pivot axis 86. Thefifth cam follower 135 is disposed adjacent to and is responsive to thecam surface 119 of the cam plate 118 carried by the intermediate plate100. One or more coolant passages may be formed in the third plate 125,or by conduits 138 extending from, through or about the third plate 125to facilitate routing coolant to and from the arms 70 and tooling 72 ofthe pellet cutter and transfer apparatus 26.

The third plate 125 preferably includes a pair of outwardly extendingflanges 140 with through holes 142 adapted to slidably receive the rods115 carried by the intermediate plate 100 so that the third plate 125and flanges 140 are slidably moved relative to the rods 115 and theintermediate plate 100. A spring 116 is preferably disposed around eachrod 115 between the flange 96 of the intermediate plate 100 and theflange 140 of the third plate 125 to yieldably bias the third plate 125relative to the intermediate plate 100. A stop block 144 is preferablycarried by the third plate 125, such as by being fixed to the supportbracket 126 for the third follower 127 or to the third plate 125.

As best shown in FIGS. 5-8 and 28-30, two sets of tooling 72 arepreferably provided on each arm 70. The tooling sets 72 are preferablylaterally spaced apart a distance equal to the spacing between theoutlets 50 of the extruder 20 such that each tooling set 72 is alignedwith a separate one of the outlets 50 of the extruder 20. Each toolingset 72 includes a mounting plate 143 fixed to the third plate 125, astationary gripper 144 carried by the mounting plate 68 and including anupstanding finger 145, and a moveable gripper 146 with a cavity 148provided between the moveable gripper 146 and the stationary gripper144. As best shown in FIGS. 5, 7 and 8, each moveable gripper 146 iscarried by a separate bracket 147 that is fixed to the lateral slide 129for movement relative to the finger 145 to vary the size of the cavity148 to facilitate receiving, carrying and releasing plastic pellets.Preferably, the movable gripper 146 includes a radiused or arcuate innersurface 150 that defines part of the cavity 148 between the moveablegripper 146 and stationary gripper 144 in which the plastic charge orpellet is received. The radiused inner surface 150 may facilitatereceiving a plastic pellet in the cavity 148, and improve the handlingof the pellet after it is received in the cavity 148. Also, the shape ofthe cavity 148 defined by the grippers 144,146 can be constructed andarranged as desired to provide a desired contact or gripping of a pelletreceived therein, and may provide at least some shaping or forming ofthe pellet if desired.

Each tooling set 72 preferably also includes a knife 154 (not shown inFIGS. 6-8) carried by the mounting plate 143 and having a thin andpreferably sharp leading edge 155 adapted to cut or shear a stream ofextruded material from the extruder 20 as the arm 70 is rotated past theoutlets 50 of the extruder 20. Fluid conduits 156 lead to passages thatare preferably formed in the moveable and stationary grippers 144,146and in the knives 154 to circulate coolant through the grippers 144,146and knives 154 in use. The tooling components are preferably formed of amaterial having high thermal conductivity to facilitate cooling them,and may be also formed from a nonstick or relatively low frictionmaterial to avoid or reduce adhesion or undue friction between theplastic pellets and the tooling 72. In one presently preferredembodiment, the knives 154 are formed from Ampco 940 to facilitate heattransfer away from the knives 154, and the grippers 144,146 are formedfrom aluminum. The grippers 144,146 may be coated to prevent or inhibitcorrosion. In one presently preferred implementation, the surfaces thatcontact the plastic pellets are preferably not coated, but may be vaporhoned or otherwise treated for improved handling and release of thepellets.

As best shown in FIGS. 5, 7 and 17-19, a gripper latch 160 is carried bythe arm 70 and associated with the tooling 72 to control at least inpart the movement of the moveable gripper 146 relative to the stationarygripper 144. The gripper latch 160 includes a generally C-shaped bracket162 that is fixed to the third plate 125 and journals for rotation ashaft 164 extending through aligned bores 166 in the bracket 162. Theshaft 164 is maintained on the bracket 162 by a pair of clamps 168 fixedto opposed ends of the shaft 164. One of the clamps 168 preferablyincludes an outwardly extending latch finger 170 adapted to engage alatch surface which may be a shoulder 172 (FIG. 8) formed in the lateralslide 129 carried by the third plate 125. When the latch finger 170 isengaged with the latch surface 172, the horizontal slide 129 isprevented from moving to prevent movement of the moveable grippers 146of the tooling 72. In one presently preferred embodiment, the otherclamp 168 includes a bracket 173 that receives a pivot shaft 174 via atrunnion mount. The trunnion mount is acted upon by a spring 176 that isoperably associated with a flange 177 (such as be a clevis arrangement)that is fixed to the C-shaped bracket 162 to yieldably bias the latchfinger 170 away from the latch surface 172 so that the gripper latch 160is normally open, or unlatched. To close the latch 160 by moving thelatch finger 170 into engagement with the latch surface 172, a sixth camfollower 179 is preferably associated with the latch finger 170 and isresponsive to the contour of a corresponding cam surface of the camsystem 74 to rotate the latch finger 170 about the axis of the shaft 164when it is desired to close the latch 160. The spring 176 may beenclosed in a retainer 178 that maintains the position and orientationof the spring 176.

A lift latch assembly 180 is preferably carried by the arm 70 toselectively prevent vertical movement of the third plate 125 relative tothe intermediate plate 100. It holds the third plate 125 up against thebias of the springs 116 tending to drive the third plate 125 down sothat when the latch 180 is released the third plate 125 drops under theforce of gravity and the force of the springs 116.

The lift latch 180 includes a main body 181 preferably fixed to theintermediate plate 100 with a shaft 182 extending through the body 181so that. opposed ends of the shaft 182 extend outwardly from the body181. A latch finger 183 is disposed on one end of the shaft 182 by anappropriate clamp 184 that may be integrally formed with the finger 183.A seventh follower 185 is coupled to the finger 183 to drive the finger183 between its latched and unlatched positions. The latch finger 183preferably includes a shoulder 186 adapted to engage a latch surface onthe third plate 125, such as a stop surface 187 (FIGS. 13 and 16) on theblock 144, to prevent downward movement of the third plate 125 when thelatch finger 183 is engaged with the latch surface 187.

At the other end of the shaft 182, a second clamp 188 is preferablyfixed to the shaft 182 and is yieldably biased by a spring 189. Thespring 189 may be received in a spring retainer 190 carried by a shaft182 that is fixed to a bracket 192 that is in turn carried by the body181. One end of the spring 189 is operably coupled to a clevis 193carried by the second clamp 188 to yieldably bias the latch finger 183into engagement with the latch surface 187. In this manner, the liftlatch 180 can be considered to be normally closed or latched and ismoved to an open position or unlatched position by engagement of theseventh follower 185 with a corresponding cam surface. To facilitateadjustment of the vertical position of the third plate 125, and hence ofthe tooling 72 carried by the third plate 125, a jack block 194 may beprovided to permit adjustment of the lift latch 180 relative to theintermediate plate 100 to thereby adjust the position in which the latchfinger 183 engages the latch surface 187 on the third plate 125.

As best shown in FIG. 24-27, the cam system 74 in one presentlypreferred embodiment includes a plurality of cam plates each includingat least one cam surface or cam track. For ease of viewing the hub 66and arms 70, the cam plates have been removed from FIGS. 2-4. A first orlower cam plate 196 is carried by a support plate and block 197 andpreferably includes a cam track 198 in which the first follower 98carried by the base plate 78 is received to control the pivotal orangular movement of the arm 70 about the pivot axis 86. This cam trackor surface 198 is preferably circumferentially continuous so that thefirst follower 98 is generally continuously engaged with the cam track198 to control the pivoted or angular movement and orientation of thearm 70.

A second cam plate 200 preferably includes a cam surface 202 or trackadapted to receive the second cam follower 110 carried by theintermediate plate 100 of the arm 70 to drive the intermediate plate 100for lateral movement relative to the base plate 78. The cam track 202 ispreferably circumferentially continuous so that the second cam follower110 is received in the cam track 202 throughout the rotation of the hub66 to maintain control of the horizontal position of the intermediateplate 100 and the third plate 125 that is carried by the intermediateplate 100. Since the arms 70 extend generally radially from the hub 66(with pivoted or angular movement relative to the hub 66), the contourof the cam surface 202 drives the second cam follower 110 and theintermediate plate 100 generally radially relative to the axis of theshaft 54 and hub 66.

A third cam plate 204 is preferably carried by a bracket 206 fixed tothe frame 36 or support 197 and includes a cam surface 208 adapted toengage the fourth follower 131 associated with the lateral slide 129.Hence, changes in the contour of this cam surface 208 drives the movablegrippers 146 relative to the stationary grippers 144 to thereby open thetooling 72 for receipt of a plastic mold charge pellet therein.

A fourth cam plate 210 is preferably carried by the frame 36 andincludes a cam surface 212 adapted to engage the third follower 127carried by the third plate 125 during a portion of each revolution ofthe hub 66 to raise the third plate 125 relative to the base plate 78and axially or vertically position the tooling 72 relative to theoutlets 50 of the extruder 20. Raising the third plate 125 preferablyengages the latch surface 187 with the latch finger 183 of the liftlatch 180 to hold the third plate 125 in its raised position.Accordingly, with the third plate 125 maintained in its raised positionby the latch 180 the arcuate extent or circumferential length of the camsurface 212 of the fourth cam plate 210 can be limited since engagementof the third follower 127 with the cam surface 212 is not needed tomaintain the vertical position of the third plate 125.

A fifth cam plate 214 is preferably carried by a bracket 216 fixed tothe frame 36 or support 197. The fifth cam plate 214 has a cam surface218 adapted to engage the seventh follower 185 that is associated withthe lift latch finger 183 to release the lift latch 180, or displace thelatch finger 183 from the latch surface 187, when desired. Preferably,in the same general area of the hub 66 and the cam system 74, a sixthcam plate 219 preferably integral with or carried by the same bracket216 that carries the fifth cam plate 214, is provided and has a camsurface 220 adapted to engage the third follower 127 carried by thethird plate 125 so that when the lift latch 180 is released, the thirdplate 125 is supported by engagement of the third follower 127 with thecam surface 220. The cam surface 220 of the sixth cam plate 219preferably is contoured to permit vertical displacement of the thirdplate 125 relative to the base plate 78, and this movement may be in adownward direction to facilitate releasing a pellet or charge of plasticfrom the tooling 72.

In one rotation of the hub 66, each pellet cutter arm 70 cuts the streamof extruded material from each of the pair of extruder outlets 50forming two pellets or plastic charges carried by arm 70 for delivery tothe compression molding machine 14. In more detail, before an arm isswept past the extruder outlets 50, the arm and associated componentsare in the following state: the sets of tooling 72 are moved to theiropen position by engagement of the fourth follower 131 (carried by thelateral slide 129) with the cam surface 208 on the third cam plate 204driving the movable grippers 146 away from their associated stationarygrippers 144; the third plate 125 is raised upwardly relative to thebase plate 78 by engagement of the third follower 127 with the camsurface 212 on the fourth cam plate 210 so that the lift latch 180 isengaged with the third plate 125 to hold it in its raised position; thecavity 148 of each gripper pair 144,146 is radially aligned with theextruder outlets 50 as controlled by engagement of the second camfollower 110 with the cam surface 202 of the second cam plate 200 whichmoves the intermediate plate 100 relative to the base plate 78; and thearm 70 is pivoted about the pivot axis 86 by engagement of the firstfollower 98 with the cam surface 198 of the first cam plate 196 so thatthe free end 73 of the arm 70 is inclined forwardly relative to a line222 (FIG. 34) extending radially from the rotational axis 56 to thefixed end 71 of the arm 70. To get into this angular position, the freeend 73 of the arm 70 is accelerated relative to the speed of rotation ofthe hub 66 as the arm 70 is pivoted.

As best shown in FIG. 34, as the arm 70 approaches the area of theextruder outlets 50, the free end 73 of the arm 70 is deceleratedrelative to the hub 66 by pivoting the arm 70 about the pivot axis 86,and the intermediate plate 100 is moved radially relative to the baseplate 78 (as controlled by engagement of the second follower 110 withthe cam surface 202 of the second cam plate 200) so that the arm 70travels in a straight line as the arm 70 is swept through the area ofthe extruder outlets 50. FIG. 34 diagrammatically illustrates threepositions of an arm 70 as it is moved through the area of the extruderoutlets 50. In position A the free end 73 of the arm 70 leads thepivoted end 71 of the arm 70 relative to the radial line 222. Inposition B the free end 73 and pivoted end 71 of the arm 70 are radiallyaligned. And in position C the free end 73 of the arm trails the pivotedend 71 of the arm 70 relative to a radial line 224 extending from theaxis 56 to the pivoted end 71 of the arm 70. This facilitates accuratelycutting the extruded material streams with the knives 154 and capturingthe cut plastic pellets in the tooling 72.

After the plastic pellets are cut from the extruded material streams,the sets of tooling 72 are closed by a suitable biasing member, such asa spring, acting on the tooling 72 to relatively quickly and preferablygently close the sets of tooling 72 on the plastic pellets. If desired,the sets of tooling 72 can compress, stretch or otherwise form theplastic pellets into a desired shape for subsequent delivery and moldingin a mold cavity 24.

With the plastic pellets captured in the sets of tooling 72, subsequentrotation of the hub 66 positions the arm 70 to deliver the plasticcharges into the mold cavities 24. To facilitate aligning the grippercavities 148 with the associated mold cavities 24, the arm 70 and camsystem 74 are constructed so that a midpoint 230 between the sets oftooling 72 on each arm 70 travels along a plane 232 during the portionof the hub 66 rotation wherein the mold charge pellets 28 carried by thesets of tooling 72 are generally aligned with the mold cavities 24. Todo this, the arm 70 is pivoted by engagement of the first follower 98with the cam surface 198 of the first cam plate 196 so that the free end73 of the arm 70 leads or is advanced forward relative to a line 234extending radially from the rotational axis 56 to the pivoted end 71 ofthe arm 70. The arm 70 is preferably inclined relative to this radialline 234 by between about 10 and 50 degrees, more preferably betweenabout 20 to 40 degrees, and most preferably about 25 to 35 degrees. Theintermediate plate 100 is also driven relative to the base plate 78 toradially align the sets of tooling 72 with the mold cavities 24.

As best shown in FIG. 35, when the arm 70 is swept through the area ofthe mold cavities 24, the free end 73 of the arm 70 is deceleratedrelative to the hub 66 by pivoting the arm 70 about the pivot axis 86,and the intermediate plate 100 is driven radially or laterally so thatthe midpoint 230 between the tooling sets 72 is moved generally alongthe plane 232. Since in one presently preferred embodiment the moldcavities 24 are radially aligned relative to the rotational axis 88 ofthe compression molding turret 16 and are moving along an arcuate pathdefined by the turret 16, the arm 70 is desirably pivoted at a rate thatis a function of the angular rotational speed of the compression moldingturret 16. This enables the cavity 148 of each gripper 72 to be axiallyaligned with an associated mold cavity 24 over an arc long enough toinitially align the pellets 28 carried by the grippers 72 with thecorresponding mold cavities 24 and deliver the plastic pellets 28 intothe mold cavities 24. Preferably, the midpoint 230 between the cavities148 of the sets of tooling 72 travels generally along the plane 232 overat least 10 to 70 degrees of hub rotation, and more preferably over 40to 50 degrees of hub rotation, although other ranges or values may beemployed for a particular application. In this range of hub rotation,the arm 70 is preferably generally radially aligned with the rotationalaxis 88 of the compression molding machine turret 16.

The plane 232 is preferably generally perpendicular to a plane 233including the rotational axis 88 of the turret 16 and the axis 56 of thehub 66, although the plane 232 can be inclined relative to the plane 233by an acute included angle of up to about 10 degrees. In the presentlypreferred embodiment, the pellets are preferably delivered into thecorresponding mold cavities during a window of hub 66 rotation thatbegins about 25 degrees before the plane 233 and continues until about25 degrees after the plane 233, over about 50 degrees of hub rotation asnoted above.

The arm 70 moves from a first position, labeled ‘D’ in FIG. 35 whereinthe free end 73 leads the pivoted end 71, through a position labeled ‘E’in FIG. 35 wherein the free end 73 of the arm 70 is radially alignedwith the pivoted end 71 and to a position ‘F’ wherein the free end 73 ofthe arm 70 trails the pivoted end 71 of the arm 70 relative to a radialline 236 extending to the pivoted end 71 of the arm 70. At the end ofthis portion of the hub rotation, the free end 73 of the arm 70 maytrail the pivoted end 71 relative to a radius 236 of the hub 66extending to the pivoted end 71 of the arm 70 by between about 15 to 45degrees, and more preferably by between 25 to 30 degrees, although otherorientations and movement of the arms 70 may be employed. In onepresently preferred embodiment, the gripper cavities 148 aresufficiently aligned with the mold cavities 24 to deliver plasticcharges into the mold cavities 24 over at least some and preferably asubstantial portion of this range of hub rotation.

When the sets of tooling 72 are aligned with the associated moldcavities 24, the third follower 127 carried by the third plate 125 isengaged with a cam surface 220 on the sixth cam plate 219 to raise thethird plate 125 relative to the intermediate plate 100 and disengage thelatch surface 187 from the lift latch finger 183. The lift latchfollower 185 is then engaged with the cam surface 218 on the fifth camplate 214 to open or release the lift latch 180 so the latch finger 183is disengaged from the third plate 125. The springs 116 bias the thirdplate 125 downwardly maintaining the third follower 127 engaged with thecam surface 220 on the sixth cam plate 219 which has a sharply axiallydeclining section permitting rapid lowering of the third plate 125relative to the base plate 78 under the force of gravity and the springs116. The downward movement of the third plate 125 moves the fifthfollower 135 relative to the cam plate 118 which is contoured to movethe lateral slide 129 in a direction driving the movable grippers 146away from their associated stationary grippers 144 to open the sets oftooling 72 at a desired rate and time and facilitate releasing theplastic pellets 28 from the sets of tooling 72 as the third plate 125 isdropping or moving axially downwardly. The cam surface 220 of the sixthcam plate 219 preferably includes a laterally extending finish section240 (FIG. 26) that stops or slows the downward travel of the third plate125 so that the downward inertia of the plastic pellets 28 ensures thatthey are released from the sets of tooling 72. In this manner, theplastic pellets 28 are transferred from the sets of tooling 72 to themold cavities 24. The downward or axial travel of the tooling 72preferably occurs over a range of between 5 and 25 degrees of hubrotation, although other arrangements may be employed. After the pelletshave been transferred to the mold cavities 24, the arm 70 is positionedas described above for movement past the extruder outlets 50 to cut andgather the next pair of mold charge pellets 28 to be delivered by thatarm 70.

In one presently preferred embodiment, the pellet cutter and transferapparatus 26 includes eight arms 70 (FIG. 4) generally evenlycircumferentially spaced about the hub 66. Accordingly, for eachrotation of the hub 66, sixteen mold charge pellets 28 are delivered.Also in one presently preferred embodiment, the compression moldingmachine 14 with which the pellet cutter and transfer apparatus 26 isused, has forty (40) mold tooling pairs 18 with each mold tooling pair18 including four (4) mold cavities 24. Thus, each rotation of the hub66 supplies the plastic charges for four (4) of the mold tooling pairs18 of the compression molding machine 14, and to fill every mold cavity24, the hub 66 must be rotated ten (10) times for each rotation of theturret 16 of the compression molding machine 14. Accordingly, the hub 66is preferably rotated at a speed that is a function of the speed ofrotation of the turret 16 of the compression molding machine 14.Preferably, the motor 58 that rotates the hub 66 is servo-controlled andcommunicated with a controller that either controls or is informed ofthe speed of rotation of the compression molding turret 16 so that thepellet cutter and transfer apparatus 26 is synchronized with thecompression molding turret 16.

Upon initial start-up of the pellet cutter and transfer apparatus 26, itmay be necessary or desirable to reject or discard a certain number ofplastic pellets. This may be necessary or desirable to ensure that theextruded material streams are flowing at a desired rate so that theplastic pellets are of the proper size and volume. To facilitaterejecting plastic pellets, the gripper latch 160, which is normallyunlatched or open, may be engaged or closed by a movable cam plate 242(FIG. 17) that is aligned with the sixth follower 179 carried by thegripper latch finger 170 only when plastic pellets are to be rejected.The gripper latch 160 holds the sets of tooling 72 open (with themovable grippers 146 moved away from the stationary grippers 144) sothat the tooling 72 does not closely engage or hold the plastic pellets.To ensure that the pellets are removed from the tooling 72, a rejectmechanism 244 (FIG. 2) can be provided downstream of the extruderoutlets 50 and axially aligned with the cavities of the sets of tooling72. The reject mechanism 244 may have, for example, one or more jet ornozzles adapted to provide a stream or burst of a pressurized fluid(such as air or water) that drives the pellets 28 to be rejected out ofthe sets of tooling 72 as they are moved past the nozzles. When it isdesired to cease rejecting plastic pellets, the reject mechanism 244 isturned off and the movable cam plate 242 is moved so that it no longerengages the sixth follower 179 of the first latch 160, which returns toits open or unlatched position 202 under the force of the spring 176 sothat the sets of tooling 72 can be closed on the pellets 28 as describedabove.

A second embodiment of a lift latch 250 is shown in FIGS. 31-33. Thislift latch 250 includes a latch finger 252 carried by the bracket 126 onthe third plate 125 that carries the third follower 127, and a slidablecatch assembly 254 carried on a bracket 256 fixed to the intermediateplate 100 of the arm 70. The latch finger 252 includes a shoulder 257adapted to be selectively engaged with a catch plate 258 of the catchassembly 254 to releasably hold the third plate 125 in a raised positionas described with reference to the first embodiment lift latch 180.

The catch assembly 254 includes a slide block 260, a support block 262,a slide 264, a cam follower 266 and the catch plate 258. The slide block262 is carried by the bracket 256 so that a bore (not shown) in theslide block 262 is aligned with a bore 272 in the support block 262. Theslide 264 preferably includes a generally cylindrical shaft portion 274slidably received in the bores of the blocks 260, 262 preferably withbearings disposed between them. One end of the slide 264 is coupled tothe cam follower 266 so that the slide 264 is driven relative to theslide block 260 in response to changes in the contour of a correspondingcam surface. The catch plate 258 is coupled to the slide 264 forco-movement with the slide 264 relative to the latch finger 252 and ispreferably slidably received in a slot 276 formed in the slide block260. The catch plate 258 and slide 264 move between a latched positionwherein the shoulder 257 of the finger 252 overlies at least a portionof the catch plate 258 and an open position wherein the catch plate 258is spaced from the latch finger 252.

When it is desired to latch the third plate 125 in a raised position tocut and receive in the tooling 72 a pair of plastic pellets, the thirdplate 125 is raised relative to the intermediate plate 100, and when theshoulder 257 of the latch finger 252 clears (i.e. is raised above) thelevel of the catch plate 258, the slide 264 may be driven toward thelatched position wherein a portion of the catch plate 258 is disposedbeneath the shoulder 257 of the latch finger 252. The third plate 125can be lowered to engage the latch finger 252 with the catch plate 258,and thereafter the third plate 125 may be supported by the latchassembly 250. To unlatch the third plate 125 so that it may be loweredto discharge the plastic pellets 28, the third plate 125 is preferablyraised slightly to disengage the latch finger 252 from the catch plate258. The slide 264 is then moved toward its open position so that thecatch plate 258 is not disposed beneath the latch finger 252 andsubsequent downward movement of the third plate 125 does not engage thelatch finger 252 with the catch plate 258.

In addition to the modified lift latch 250, the arm 70 may be modifiedas shown in FIGS. 31-33, to include an extended flange 280 on theintermediate plate 100 with an opening 282 that receives a shaft 284about which a spring 286 is provided. One end of the spring 286 engagesthe flange 280 and the other end of the spring 286 engages a flange 288extending from the bracket 126 on the third plate 125. In this manner,the third plate 125 is yieldably biased axially downwardly relative tothe intermediate plate 100 of the arm 70. The spring 286 of thisembodiment may be used in addition to or may replace one or both of thesprings 116 disposed between the intermediate plate 100 and the thirdplate 125 as set forth above.

As best shown in FIG. 36, another cam follower 290 may be carried on thearm 70, preferably by the third plate 125. The cam follower 290preferably rotates about a shaft carried by a bracket 292 fixed to thethird plate 125. The shaft preferably extends generally perpendicular tothe pivot axis 86 and parallel to the lateral movement of theintermediate plate 100 relative to the base plate 78. The cam follower290 is adapted to engage a cam surface 294 of a cam plate 296 providedbetween the extruder heads to provide a consistent axial positionreference for the tooling 72, and specifically for the knives 154relative to the extruder outlets 50. The cam follower 290 also supportsthe arm 70 against torsional forces tending to twist the arm 70 such asmay be caused by deceleration of the free end 73 of the arm 70 as it isswept past the extruder outlets 50.

While certain preferred embodiments and constructions and arrangementsof particular components of the compression molding apparatus, thepellet cutter and transfer apparatus and method of delivering moldcharge pellets to a mold cavity have been shown and described herein,one of ordinary skill in this art will readily understand thatmodifications and substitutions can be made without departing from thespirit and scope of the invention as defined by the appended claims. Forexample, without limitation, while in the presently preferredembodiments two extrudate streams are provided to enable simultaneousdelivery of two mold charge pellets, the invention can be practiced todeliver a single mold charge pellet or more than two mold chargepellets. Of course, other modifications and substitutions will beapparent from this disclosure. Further, relative adjectives like“upper,” “lower,” “central,” “downward”, and the like are used todescribe features of the apparatus and method with respect to theposition and orientation of such features as shown in the accompanyingdrawings of the presently preferred embodiments.

1. Apparatus for compression molded plastic articles, which includes: aplurality of molds mounted for endless motion around a first axis, eachof said molds including a first section and a second section, at leastone of which is movable with respect to the other in a directionparallel to said first axis to form a mold cavity, and a pellet cutterand transfer apparatus for forming individual mold charge pellets from asource of plastic material and delivering the individual mold chargepellets to said mold cavities, said apparatus including: a hubrotational around a second axis parallel to said first axis, at leastone arm extending generally radially from said hub to rotate with saidhub around said second axis, and a cam system extending at leastpartially around said second axis and operatively coupled to said armfor moving said arm in at least one predetermined direction with respectto said second axis as said hub and said arm rotate around said secondaxis.
 2. The apparatus set forth in claim 1 wherein said cam systemincludes a cam arrangement for moving said arm radially inwardly andoutwardly with respect to said second axis as a function of rotationaround said second axis.
 3. The apparatus set forth in claim 1 whereinsaid cam system includes a cam arrangement for moving said arm angularlywith respect to said hub as a function of rotation of said hub and saidarm around said second axis.
 4. The apparatus set forth in claim 1wherein said cam system includes a cam arrangement for moving said armaxially parallel to said second axis as a function of rotation aroundsaid second axis.
 5. The apparatus set forth in claim 1 wherein said camsystem includes a cam arrangement for moving said arm radially inwardlyand outwardly with respect to said second axis as a function of rotationaround said second axis, and for moving said arm angularly with respectto said hub as a function of rotation of said hub and said arm aroundsaid second axis.
 6. The apparatus set forth in claim 1 wherein said camsystem includes a cam arrangement for moving said arm radially inwardlyand outwardly with respect to said second axis as a function of rotationaround said second axis and for moving said arm axially parallel to saidsecond axis as a function of rotation around said second axis.
 7. Theapparatus set forth in claim 1 wherein said cam system includes a camarrangement for moving said arm angularly with respect to said hub as afunction of rotation of said hub and said arm around said second axisand for moving said arm axially parallel to said second axis as afunction of rotation around said second axis.
 8. The apparatus set forthin claim 1 wherein said cam system includes a cam arrangement for movingsaid arm radially, axially and angularly with respect to said secondaxis as a function of rotation around said second axis.
 9. The apparatusset forth in claim 1 wherein said arm includes a pivot shaft carried bythe hub and defining a pivot axis about which the arm is pivoted, saidpivot axis being parallel to said second axis.
 10. The apparatus setforth in claim 9 wherein the arm includes a base plate that is operablyconnected to the pivot shaft.
 11. The apparatus set forth in claim 10wherein the arm includes a slide plate carried by the base plate formovement along the base plate generally radially with respect to saidsecond axis, said slide plate being responsive to the contour of a camsurface of the cam system to drive the slide plate relative to the baseplate.
 12. The apparatus set forth in claim 10 wherein the arm includesa plate carried by the base plate for movement along the base plategenerally axially with respect to said second axis, said plate beingresponsive to the contour of a cam surface of the cam system to controlmovement of the plate relative to the base plate.
 13. The apparatus setforth in claim 10 wherein the arm includes an intermediate plate carriedby the base plate for radial movement relative to the base plate and athird plate carried by the intermediate plate for movement with theintermediate plate relative to the base plate, and said third platebeing movable relative to the intermediate plate in a direction parallelto the pivot axis.
 14. The apparatus set forth in claim 1 which alsoincludes a pair of tooling assemblies carried by the arm and spaced fromeach other with each tooling assembly adapted to carry a separate moldcharge pellet, and wherein each mold includes at least a pair ofradially aligned mold cavities, said arm being moved relative to saidhub so that a point midway between the tooling assemblies moves in aplane during a portion of the hub rotation to facilitate aligning themold charge pellets carried by the tooling assemblies.
 15. The apparatusset forth in claim 14 wherein said plane is perpendicular to a planethat includes the first axis and second axis.
 16. The apparatus setforth in claim 15 wherein during the portion of the hub rotation whereinsaid point midway between the tooling assemblies moves in said planesaid point intersects said plane that includes the first axis and thesecond axis.
 17. The apparatus set forth in claim 14 wherein during saidportion of hub rotation the arm is moved angularly and radially relativeto the hub.
 18. The apparatus set forth in claim 17 wherein the arm isalso moved axially relative to the hub to facilitate releasing the moldcharge pellets from the tooling assemblies.
 19. The apparatus set forthin claim 18 wherein said arm includes a base plate pivotally carried bythe hub, an intermediate plate carried by the base plate for radialmovement relative to the base plate, and a third plate carried by theintermediate plate for axial movement relative to the intermediateplate.
 20. The apparatus set forth in claim 19 wherein each of the baseplate, intermediate plate and third plate includes at least one followerengageable with a cam surface of the cam system to control the movementof the base plate, intermediate plate and third plate relative to thehub.
 21. The apparatus set forth in claim 1 wherein said arm includes atleast one tooling assembly including a stationary gripper carried by thearm and a movable carried gripper carried by the arm for movementrelative to the stationary gripper, said movable gripper being operablyconnected to a cam follower that is responsive to the cam system todrive the movable gripper relative to the stationary gripper.
 22. Theapparatus set forth in claim 21 wherein said arm includes two spacedapart tooling assemblies each including a movable gripper and astationary gripper, each movable gripper being operably connected to thesame cam follower for co-movement of the movable gripper of each toolingassembly.
 23. The apparatus set forth in claim 22 which also includes alateral slide carried by the arm, said cam follower being carried by thelateral slide with each movable gripper operably connected to thelateral slide.
 24. The apparatus set forth in claim 23 which alsoincludes a second cam follower carried by the lateral slide andresponsive to the contour of an associated cam surface to move thelateral slide in a direction moving the movable grippers away from theirassociated stationary gripper.
 25. The apparatus set forth in claim 24which also includes a plate carried by the arm for movement parallel tothe second axis, said lateral slide being carried by said plate formovement in a direction perpendicular to said second axis and saidsecond follower being moved along its associated cam surface when saidplate is moved relative to the arm.
 26. The apparatus set forth in claim25 which also includes at least one spring operably associated with saidplate to yieldably bias the plate axially downwardly so that the platemoves downwardly under the combined forces of gravity and the spring.27. The apparatus set forth in claim 12 which also includes at least onespring operably associated with said plate to yieldably bias the plateaxially downwardly so that the plate moves downwardly under the combinedforces of gravity and the spring.
 28. The apparatus set forth in claim19 which also includes at least one spring disposed between theintermediate plate and the third plate to yieldably bias the third plateaxially downwardly so that the plate moves downwardly under the combinedforces of gravity and the spring.
 29. The apparatus set forth in claim12 which includes a latch selectively associated with said plate tomaintain an axial position of the plate.
 30. The apparatus set forth inclaim 19 which includes a latch selectively associated with said thirdplate to maintain an axial position of the third plate.
 31. Theapparatus set forth in claim 30 wherein said latch is yieldably biasedto an open position wherein the latch does not interfere with axialmovement of the third plate, and is moved to a closed position tomaintain the third plate in an axially raised position to preventdownward axial movement of the third plate until the latch is moved toits open position.
 32. The apparatus set forth in claim 31 which alsoincludes a cam follower coupled to the latch to move the latch from itsopen position to its closed position.
 33. The apparatus set forth inclaim 21 wherein at least one of the grippers includes an arcuate innersurface that defines a portion of a cavity in which a mold charge pelletis received.
 34. The apparatus set forth in claim 33 wherein the movablegripper includes an arcuate inner surface.
 35. The apparatus set forthin claim 21 wherein the movable gripper and the stationary gripperdefine a cavity in which a mold charge pellet is received and themovable gripper is movable relative to the stationary gripper from anopen position wherein said cavity has its largest volume to a closedposition wherein said cavity has its smallest volume, and in said closedposition said grippers engage and retain a mold charge pellet in thecavity.
 36. The apparatus set forth in claim 35 which also includes alatch selectively associated with the movable gripper, the latch havingan open position wherein it does not interfere with movement of themovable gripper and a closed position wherein the latch holds themovable gripper in its open position.
 37. The apparatus set forth inclaim 36 which also includes a reject mechanism disposed adjacent to thepath of movement of the arms as the hub rotates and operable to displacemold charge pellets from the grippers when it is desired to reject themold charge pellets rather than deliver them to the mold cavities. 38.The apparatus set forth in claim 37 wherein the reject mechanismincludes a fluid nozzle that directs fluid under pressure onto the moldcharge pellets to displace the mold charge pellets from the grippers.39. The apparatus set forth in claim 21 wherein each tooling assemblyincludes a knife disposed axially above the grippers. 40.-48. (canceled)49. Apparatus for transferring a mold charge pellet to a molding machinehaving a mold with a mold cavity, including: a hub rotated about anaxis, at least one arm extending generally radially from said hub torotate with said hub around said axis, and a cam system extending atleast partially around said axis and operably coupled to said arm formoving said arm along a predetermined path with respect to said axis assaid hub and said arm rotate around said axis, at least a portion ofsaid arm traveling along a plane that is parallel to said axis during aportion of said path.
 50. The apparatus set forth in claim 49 whereinsaid cam system includes a cam arrangement for moving said arm radiallyinwardly and outwardly with respect to said axis as a function ofrotation around said axis.
 51. The apparatus set forth in claim 49wherein said cam system includes a cam arrangement for moving said armangularly with respect to said hub as a function of rotation of said huband said arm around said axis.
 52. The apparatus set forth in claim 49wherein said cam system includes a cam arrangement for moving said armaxially parallel to said axis as a function of rotation around saidaxis.
 53. The apparatus set forth in claim 49 wherein said cam systemincludes a cam arrangement for moving said arm radially inwardly andoutwardly with respect to said axis as a function of rotation aroundsaid axis, and for moving said arm angularly with respect to said hub asa function of rotation of said hub and said arm around said axis. 54.The apparatus set forth in claim 49 wherein said cam system includes acam arrangement for moving said arm radially inwardly and outwardly withrespect to said axis as a function of rotation around said axis and formoving said arm axially parallel to said axis as a function of rotationaround said axis.
 55. The apparatus set forth in claim 49 wherein saidcam system includes a cam arrangement for moving said arm angularly withrespect to said hub as a function of rotation of said hub and said armaround said axis and for moving said arm axially parallel to said axisas a function of rotation around said axis.
 56. The apparatus set forthin claim 49 wherein said cam system includes a cam arrangement formoving said arm radially, axially and angularly with respect to saidaxis as a function of rotation around said axis.
 57. The apparatus setforth in claim 49 wherein said arm includes a pivot shaft carried by thehub and defining a pivot axis about which the arm is pivoted, said pivotaxis being parallel to said axis.
 58. The apparatus set forth in claim57 wherein the arm includes a base plate that is operably connected tothe pivot shaft.
 59. The apparatus set forth in claim 58 wherein the armincludes a slide plate carried by the base plate for movement along thebase plate generally radially with respect to said axis, said slideplate being responsive to the contour of a cam surface of the cam systemto drive the slide plate relative to the base plate.
 60. The apparatusset forth in claim 58 wherein the arm includes a plate carried by thebase plate for movement along the base plate generally axially withrespect to said axis, said plate being responsive to the contour of acam surface of the cam system to control movement of the plate relativeto the base plate.
 61. The apparatus set forth in claim 58 wherein thearm includes an intermediate plate carried by the base plate for radialmovement relative to the base plate and a third plate carried by theintermediate plate for movement with the intermediate plate relative tothe base plate, and said third plate being movable relative to theintermediate plate in a direction parallel to the pivot axis.
 62. Theapparatus set forth in claim 49 which also includes a pair of toolingassemblies carried by the arm and spaced from each other with eachtooling assembly adapted to carry a separate mold charge pellet andwherein each mold includes at least a pair of radially aligned moldcavities, said arm being moved relative to said hub so that a pointmidway between the tooling assemblies moves in a plane during a portionof the hub rotation to facilitate aligning the mold charge pelletscarried by the tooling assemblies.
 63. The apparatus set forth in claim62 wherein the molding machine includes an axis parallel to said axis ofthe hub and about which said mold-cavity is rotated, said plane beingperpendicular to a plane that includes the axis of the hub and the axisof the molding machine.
 64. The apparatus set forth in claim 63 whereinduring the portion of the hub rotation wherein said point midway betweenthe tooling assemblies moves in said plane said point intersects saidplane that includes the axis of the hub and the axis of the moldmachine.
 65. The apparatus set forth in claim 62 wherein during saidportion of hub rotation the arm is moved angularly and radially relativeto the hub.
 66. The apparatus set forth in claim 65 wherein the arm isalso moved axially relative to the hub to facilitate releasing the moldcharge pellets from the tooling assemblies.
 67. The apparatus set forthin claim 66 wherein said arm includes a base plate pivotally carried bythe hub, an intermediate plate carried by the base plate for radialmovement relative to the base plate, and a third plate carried by theintermediate plate for axial movement relative to the intermediateplate.
 68. The apparatus set forth in claim 67 wherein each of the baseplate, intermediate plate and third plate includes at least one followerengageable with a cam surface of the cam system to control the movementof the base plate, intermediate plate and third plate relative to thehub.
 69. The apparatus set forth in claim 49 wherein said arm includesat least one tooling assembly including a stationary gripper carried bythe arm and a movable carried gripper carried by the arm for movementrelative to the stationary gripper, said movable gripper being operablyconnected to a cam follower that is responsive to the contour of a camsurface of the cam system to drive the movable gripper relative to thestationary gripper.
 70. The apparatus set forth in claim 69 wherein saidarm includes two spaced apart tooling assemblies each including amovable gripper and a stationary gripper, each movable gripper beingoperably connected to the same cam follower for co-movement of themovable gripper of each tooling assembly.
 71. The apparatus set forth inclaim 60 which also includes at least one spring operably associatedwith said plate to yieldably bias the plate axially downwardly so thatthe plate moves downwardly under the combined forces of gravity and thespring.
 72. The apparatus set forth in claim 67 which also includes atleast one spring disposed between the intermediate plate and the thirdplate to yieldably bias the third plate axially downwardly so that theplate moves downwardly under the combined forces of gravity and thespring.
 73. The apparatus set forth in claim 67 which includes a latchselectively associated with said third plate to maintain an axialposition of the third plate.
 74. The apparatus set forth in claim 73wherein said latch is yieldably biased to an open position wherein thelatch does not interfere with axial movement of the third plate, and ismoved to a closed position to maintain the third plate in an axiallyraised position to prevent downward axial movement of the third plateuntil the latch is moved to its open position.
 75. The apparatus setforth in claim 74 which also includes a cam follower coupled to thelatch to move the latch from its open position to its closed position.76.-77. (canceled)
 78. Apparatus for delivering mold charges, including:a hub rotational around an axis, at least one arm extending generallyradially from said hub to rotate with said hub around said axis, and acam system extending at least partially around said axis and operativelyassociated with said arm for moving said arm in a predetermineddirection with respect to said axis as said hub and said arm rotatearound said axis.
 79. The apparatus of claim 78 wherein said cam systemmoves said arm radially relative to said axis.
 80. The apparatus ofclaim 78 wherein said cam system moves said arm angularly relative tosaid hub.
 81. The apparatus of claim 78 wherein said cam system movessaid arm axially relative to said axis.
 82. The apparatus of claim 78wherein said cam system moves said arm radially and axially relative tosaid axis.
 83. The apparatus of claim 78 wherein said cam system movessaid arm angularly relative to said hub and axially relative to saidaxis.
 84. The apparatus of claim 78 wherein said cam system moves saidarm radially relative to said axis and angularly relative to said hub.